Collecting tank of a heat exchanger

ABSTRACT

A collecting tank of a heat exchanger may include a first collecting pipe and a second collecting pipe arranged adjacent to the first collecting pipe structured to accommodate a plurality of heat exchanger pipes. The first collecting pipe and the second collecting pipe may each have a hollow space which is flowable through. The first collecting pipe and the second collecting pipe may have a respective flattened bottom and a plurality of tank accommodations configured to accommodate the plurality of heat exchanger pipes disposed spaced apart from one another in the respective bottom. The respective bottom of the first collecting pipe and the second collecting pipe may extend at a predetermined angle α not equal to 180° relative to one another.

CROSS-REFERENCE TO RELATED APPLICATION

This application claims priority to German Application No. DE 10 2017218 810.3 filed on Oct. 20, 2017, the contents of which are herebyincorporated by reference in its entirety.

TECHNICAL FIELD

The present invention relates to a collecting tank of a heat exchanger,in particular of an evaporator. The invention furthermore relates to aheat exchanger comprising such a collecting tank.

BACKGROUND

Heat exchangers serve the purpose of exchanging heat between two fluids.One of these fluids typically flows via a collecting tank through heatexchanger pipes, around which the other fluid flows, so that heat isexchanged between the two fluids. As a result of the temperaturedifferences, which thus arise, condensate accumulates inside the heatexchanger, in particular when a gas, for example air, flows around theheat exchanger pipes. This accumulating condensate needs to bedischarged, so as to attain an interruption-free operation of the heatexchanger and/or an increased efficiency of the heat exchanger.

A heat exchanger comprising a collecting tank is known from CA 2 123 368A1, which has two collecting pipes, each comprising a bottom, in whichheat exchanger pipes, which are embodied as flat pipes, areaccommodated. To collect and discharge accumulating condensate, aseparate condensate tank, which has a w-shaped cross section comprisingopenings for discharging the condensate, is arranged on the side of thecollecting tank facing away from the heat exchanger pipes. The heatexchanger thereby requires a larger installation space and theproduction thereof is more expensive and/or more complicated. Inaddition, the heat exchanger has an increased weight.

U.S. Pat. No. 7,971,636 B2 as well as U.S. Pat. No. 7,231,966 B2 showcollecting tanks of heat exchangers, which are provided with grooves inthe form of indentations or deformations, so as to be able to betterdischarge the accumulating condensate. In U.S. Pat. No. 7,231,966 B2,the grooves are arranged laterally on the bottoms of the collecting tankand offset to the heat exchanger pipes. In U.S. Pat. No. 7,971,636 B2,the grooves are introduced into the respective bottom and surround theaccommodations for accommodating the heat exchanger pipes. Theintroduction of the grooves requires an extensive machining, for exampledeforming, of the collecting tank, in particular of the bottoms, andleads to additional production steps, which, in turn, make theproduction of the collecting tanks and thus of the heat exchanger,complicated and/or expensive.

A collecting tank of a heat exchanger is known from DE 11 2005 000 423T5, in the case of which the bottoms of the collecting tank are in eachcase embodied so as to be curved and are provided with grooves, so as tobe able to better discharge condensate. This also leads to an extensiveand/or expensive production of the collecting tank and thus of the heatexchanger. This furthermore leads to an uneven contact between thebottoms and the heat exchanger pipes and a larger installation space isrequired.

SUMMARY

The present invention thus deals with the object of at least reducingthe above-mentioned disadvantages and of specifying improved or at leastalternative embodiments for a collecting tank of a heat exchangers aswell as for such a heat exchanger, which are in particular characterizedby a simplified production and/or an increased efficiency and/or areduced installation space requirement and/or an improved transport ofaccumulating condensate.

This object is solved according to the invention by means of the subjectmatter of the independent claim(s). Advantageous embodiments are thesubject matter of the dependent claim(s).

The present invention is based on the general idea of, in the case of acollecting tank of a heat exchanger, which has two adjacent collectingpipes each comprising a bottom, wherein accommodations for accommodatingheat exchanger pipes of the heat exchanger are provided in therespective bottom, to arrange the bottoms at an incline relative to oneanother in the manner of a gabled roof or of an upside-down channel,respectively, so that the entire surface of the respective bottomoutside of the accommodations or of the heat exchanger pipes,respectively, is on principle used for a specific and improved drainageof condensate, which arises on the bottom. A larger surface is therebyavailable for discharging the condensate, so that condensate can bedischarged in an improved manner as a whole and an improved efficiencyof the collecting tank or of the heat exchanger, respectively, is thusattained. In addition, recesses or indentations, respectively, in thecollecting tank for discharging the condensate are not necessary, sothat, on the one hand, the production of the collecting tank and thus ofthe heat exchanger is simplified and becomes more cost-efficient and, onthe other hand, a smaller volume is sufficient for the condensatedischarge, so that the collecting tank and the heat exchanger can beproduced more cost-efficiently and so as to save more installationspace. According to the idea of the invention, the collecting tank hasthe two collecting pipes, which are arranged adjacently, in particularso as to adjoin one another. The respective collecting pipe has aflattened pipe bottom or bottom, in short, in which said accommodationsfor accommodating the heat exchanger pipes are embodied and are arrangedat a distance from one another. The heat exchanger pipes can thereby beflat pipes, so that the respective accommodation is embodied so as to beelongated. The collecting pipes each have a hollow space, which isfluidically connected to the heat exchanger pipes via theaccommodations, so that the heat exchanger pipes are supplied with afluid, for example coolant, via the respective collecting pipe. Thismeans that the fluid flows into the heat exchanger pipes via thecollecting tank or the collecting pipes, respectively, and/or that thefluid flows from the heat exchanger pipes into the collecting tank, inparticular into at least one of the collecting pipes. According to theinvention, the bottoms run at an inline to one another. The bottomsthereby form an angle α of not equal to 180°.

The incline of the bottoms preferably applies in installation positionof the collecting tank or of the heat exchanger, respectively, relativeto the gravitational direction, so that accumulating condensate can flowalong the respective bottom as a result of the incline. This means inparticular that the respective bottom in installation positionpreferably does not form a right angle with the gravitational direction.The incline of the bottoms further applies such that they are inclinedin the cross section, in particular evenly.

It is preferred when the bottoms are each embodied as a flat platecomprising the respective accommodations. This allows for a particularlycost-efficient production of the collecting tank as well as an efficientdischarge of accumulating condensate.

Embodiments, in the case of which the bottoms, which are inclinedtowards one another, draw and form an angle α between 177° and 171°,preferably of 174° relative to one another, prove to be advantageous.Such an angle has proven to be capable of being realized particularlyeasily and particularly effectively for discharging the accumulatingcondensate. In addition, the collecting tank can be produced in aninstallation space-saving manner with such an angle. However, smallerangles α are conceivable as well. The angle α is preferably attained inthat the respective bottom in installation position relative to theperpendicular course to the gravitational direction differs by at least1.5°, in particular by 3°, is inclined to the gravitational directionbetween 85.5° and 88.5°, in particular by 87°.

On principle, the incline of the bottoms relative to one another isembodied arbitrarily. It is conceivable that the bottoms are inclinedall the way to the corresponding hollow space. In this case, the bottomsthus form the angle α on the side facing the hollow space, or the angleis α>180°, respectively, provided that it is measured on the side facingaway from the hollow space.

Alternatives, in the case of which the bottoms are inclined away fromthe corresponding hollow space, are also conceivable. The bottomsthereby form the angle α on the side facing away from the hollow space,or the angle is α>180°, provided that it is measured on the side facingthe hollow space.

A fluid, which flows through the corresponding heat exchanger duringoperation, can flow through the hollow space of the respectivecollecting pipe, in particular a coolant. A flow cross section of therespective collecting pipe is thereby preferably bounded or formed,respectively, by the bottom and a wall connected to the bottom.

Alternatives, in the case of which the wall has a circular section inthe shape of a circular segment located opposite the correspondingbottom and transition sections connected thereto on both sides, whichtransition into the bottom, thereby prove to be advantageous. Therespective transition section is thereby formed and embodied in such away that the circular section, together with the transition sections,bounds or defines an Ω-shaped flow cross section or a flow cross sectionclose thereto, respectively. This allows in particular to realize afluidic supply of the collecting pipe, which preferably takes place atan end of the collecting pipe or on the front side of the collectingpipe, respectively, or of the collecting tank, in a particularlyeffective manner and with reduced pressure losses.

The accommodations of the respective collecting pipe, hereinafter alsoreferred to as tank accommodations, can on principle be embodiedarbitrarily. The tank accommodations of the respective collecting tankare preferably arranged spaced apart in the longitudinal direction ofthe collecting pipe. It is furthermore preferred when the tankaccommodations are formed by passages of the bottom. This allows inparticular for a fluid-tight and/or stable connection of the bottom andthus of the collecting pipe or of the collecting tank, respectively,with the heat exchanger pipes, in particular flat pipes, accommodatedtherein.

It is advantageous when the passages of at least one of the bottoms aredirected to the outside and thus away from the corresponding hollowspace. This means that the passages do not penetrate into the hollowspace, but protrude to the outside from the bottom relative to thehollow space. This in particular has the result that the portion insidethe respective collecting pipe, which can be flown through, isincreased, so that the respective collecting pipe and thus thecollecting tank as a whole can be produced to be smaller and thus in amore installation space-saving manner. The increased portion, which canbe flown through, likewise leads to an increased efficiency of thecorresponding heat exchanger.

It is preferred when the passages are produced by a ripping of thebottom, thus when they are in particular ripped to the outside. Thisallows for a cost-efficient production of the collecting tank and for anoptimized use of the available volume.

Embodiments, in the case of which the passages protrude from thecorresponding bottom by less than 3 mm, are considered to be preferred.The passages thus have a height of less than 3 mm. Heights of less than2.5 mm and 2.2 mm are particularly preferred, a height of 2 mm is verymuch preferred.

Embodiments, in the case of which at least one of the passages,preferably the respective passage, has a front side, which faces awayfrom the corresponding bottom and which runs in a curved manner, proveto be advantageous. The curved course thereby applies in particular inthe transverse direction or transversely to the distance direction ofthe passages, respectively. Particularly preferably, the front sides arecurved convexly relative to the corresponding bottom in such a way thata central area of the front side is spaced apart farther from the bottomthan outer areas of the passage, which run in the transverse direction.Such a curved course of the passage or of the front side, respectively,allows in particular to contact corrugated fins arranged in the heatexchanger between the heat exchanger pipes at the further areas of thefront sides, which protrude from the bottom, with the heat exchangerpipes and the front sides, and to thus provide an enlarged contact areabetween the corrugated fins and the heat exchanger pipes, so that theheat exchanger as a whole has an increased efficiency and/or can beproduced in a more installation space-saving manner.

To mechanically reinforce the collecting tank, in particular therespective collecting pipe, the collecting tank can be provided withbeads, in particular reinforcing beads. The respective collecting pipeis preferably provided with a plurality of such beads, which areadvantageously introduced so as to be located opposite to the bottom, inparticular in the wall, preferably in the circular section. In addition,the beads of the respective collecting pipe are advantageously spacedapart in the distance direction of the corresponding tank accommodationsand thus in particular in the longitudinal direction. This provides fora particularly effective and simple mechanical stabilizing of thecollecting tank.

It is particularly advantageous when both collecting pipes have suchbeads, wherein one bead of the first collecting pipe and one bead of thesecond collecting pipe each touch one another in an area between bothcollecting pipes or are in mechanical contact, respectively. The beads,which touch one another, can in particular run in parallel. Such anembodiment of the collecting tank has proven to be particularly stable.This mechanical stability is improved when the area between the twocollecting pipes is a central seam of the collecting tank, at which thewalls of the collecting pipes, in particular a transition section of oneof the collecting pipes, is in contact with the transition section ofthe other collecting pipe. A mechanical stabilization is therebyattained across an increased height of the collecting tank.

On principle, the collecting pipes of the collecting tank can beproduced separately and can subsequently be attached to one another, inparticular connected to one another.

Preferred embodiments provide for the integral production of bothcollecting pipes, in particular of the entire collecting tank. Thecollecting pipes are thus produced monolithically or of the same basematerial, respectively. The collecting pipes can in particular be madeof one sheet metal part, in particular by forming the sheet metal part.The collecting pipes are thus in particular made of the same sheet metalpart, which is processed to produce the collecting pipes, in particulardeformed, and which is provided with the collecting tank accommodations.The collecting tank, in particular the inclined course of the bottoms,can thus be realized in a cost-efficient and simple manner. In addition,the tank accommodations can thus be introduced into the respectivebottom in a simplified manner. The sheet metal part can have a thicknessof less than 1.2 mm, for example 1 mm or less, for example 0.9 mm orless, in particular between 0.8 mm and 0.9 mm, for example 0.8 mm.

It goes without saying that, in addition to the collecting tank, a heatexchanger comprising such a collecting tank also belongs to the scope ofthis invention. The heat exchanger thereby has at least one suchcollecting tank, which accommodates heat exchanger pipes of the heatexchanger, in particular flat pipes, via the tank accommodations of thecollecting pipes. The collecting pipes of the at least one collectingtank, together with the heat exchanger pipes, form a first duct systemof the heat exchanger, through which a first fluid, in particularcoolant, flows. The heat exchanger pipes are arranged spaced apartrelative to one another and thus form a second duct system for a secondfluid, in particular for a gas, for example for air, wherein the secondfluid exchanges heat with the first fluid, which flows through the heatexchanger pipes, via the second duct system via the heat exchangerpipes, if applicable via corrugated fins arranged between the heatexchanger pipes.

On principle, the heat exchanger can be used arbitrarily. The heatexchanger is in particular an evaporator, which is used in an airconditioning system, for example of a motor vehicle.

Further important features and advantages of the invention follow fromthe subclaims, from the drawings, and from the corresponding figuredescription by means of the drawings.

It goes without saying that the above-mentioned features, and thefeatures, which will be described below, cannot only be used in therespective specified combination, but also in other combinations oralone, without leaving the scope of the present invention.

Preferred exemplary embodiments of the invention are illustrated in thedrawings and will be described in more detail in the description below,wherein identical reference numerals refer to identical or similar orfunctionally identical components.

BRIEF DESCRIPTION OF THE DRAWINGS

In each case schematically,

FIG. 1 shows a highly simplified, circuit diagram-like illustration ofan air conditioning system in a vehicle,

FIG. 2 shows an isometric partial view of a heat exchanger of the airconditioning system comprising a collecting tank and a connectorassembly,

FIG. 3 shows a cross section through the heat exchanger in partial view,

FIG. 4 shows a cross section of the collecting tank,

FIG. 5 shows an isometric partial view of the collecting tank,

FIG. 6 shows an isometric partial view of the heat exchanger comprisingthe connector assembly in exploded illustration,

FIG. 7 shows a partial view of the heat exchanger,

FIG. 8 shows a cross section through the connector assembly in a furtherexemplary embodiment.

DETAILED DESCRIPTION

An air conditioning system 1, which can be used in a vehicle 2, so as toclimatize for example a vehicle interior 3 of the vehicle 2, isillustrated in FIG. 1 in a highly simplified manner. The airconditioning system 1 has a circuit 4, in which a coolant is driven by aconveying device 5 and circulates. The coolant thereby flows through acapacitor 6, an expander 7, as well as an evaporator 8 in succession,wherein the capacitor 6 and the evaporator 8 in each case act as a heatexchanger 9. The coolant and a further fluid flows through therespective heat exchanger 9 in such a way that a heat exchange resultsbetween the coolant and the further fluid. In the case of the evaporator8, the further fluid is air 10, which flows through the evaporator 8 andis cooled thereby, wherein the cooled air 10 is supplied to the vehicleinterior 3.

FIG. 2 shows an isometric partial view of one of the heat exchangers 9,in particular of the evaporator 8. The heat exchanger 9 has a pluralityof heat exchanger pipes 11, through which the coolant flows and whichare arranged spaced apart from one another. In the shown example, theheat exchanger pipes 11 are embodied as flat pipes 12. As a result ofthe spaced-apart arrangement of the heat exchanger pipes 11, air 10 canflow between the heat exchanger pipes 11 and can thereby flow aroundthem and can hereby exchange heat with the coolant, which flows throughthe heat exchanger pipes 11, and can thus be cooled. An improved heatexchange between the air 10 and the coolant can be attained in thatcorrugated fins 13, which can be flown through between adjacent heatexchanger pipes 11, are provided. The fluidic supply of the heatexchanger pipes 11 with the coolant takes place with the help of atleast one collecting tank 14, wherein a collecting tank 14 can be seenat an upper end of the heat exchanger 8 in FIG. 2. At an opposite lowerend, which is not shown, the heat exchanger 9 preferably has a furthersecond collecting tank 14, which is not shown.

As follows from a combined view of FIG. 2 and FIG. 3, in which thecorrugated fin 13 is suggested by a dashed line course and isillustrated in a transparent manner, the collecting tank 14 has twocollecting pipes 15, 16, namely a first collecting pipe 15, and a secondcollecting pipe 16. On the side facing the heat exchanger pipes 11, therespective collecting pipe 15, 16 has a flattened pipe bottom 17, orbottom 17 in short. A wall 18 of the corresponding collecting pipe 15,16, which bounds a hollow space 19 of the collecting pipe 15, 16, whichcan be flown through, with the bottom 17, connects at the respectivebottom 17. The collecting pipes 15, 16 each run in a longitudinaldirection 20 and thus essentially in parallel and are arranged adjacentto one another in a transverse direction 21, which runs transversely tothe longitudinal direction 20, in particular so as to adjoin one anotherdirectly. The walls 18 of the collecting pipes 14, 15 thereby meet in acentral area 22 of the collecting tank 14 in the transverse direction21, and thus form a central seam 23 of the collecting tank 14, which isarranged centrally in the transverse direction 21 and which extends inthe longitudinal direction 20. In the bottom 17, the respectivecollecting pipe 15, 16 has accommodations 24 for the heat exchangerpipes 11, which will also be identified below as tank accommodations 24.The tank accommodations 24 of the respective collecting pipe 14, 15 arespaced apart in the longitudinal direction 20 and in each caseaccommodate a heat exchanger pipe 11. In the shown example, the tankaccommodations 24 of both collecting pipes 14, 15 are thereby arrangedequidistant in the longitudinal direction 20, wherein a tankaccommodation 24 of the second collecting pipe 16 is arranged adjacentto the respective tank accommodation 24 of the first collecting pipe 15in the transverse direction 21 in such a way that two heat exchangerpipes 11, which are aligned with one another and which are spaced apartfrom one another in each case, are arranged in the transverse direction21 and that this arrangement repeats itself in the longitudinaldirection 20.

In the shown example, the coolant, which flows into the first collectingpipe 15 and in the heat exchanger pipes 11, which are arranged in thetank accommodations 24 of the first collecting pipe 15 and are thusfluidically connected thereto, is supplied to the first collecting pipe15 via a connector assembly 25. The coolant flows through these heatexchanger pipes 11 and, in particular in the non-illustrated, opposite,lower or second collecting tank 14, respectively, is deflected into theheat exchanger pipes 11, which are accommodated in the tankaccommodations 24 of the second collecting pipe 16, so that the coolantsubsequently flows via these heat exchanger pipes 11 into the secondcollecting pipe 16, wherein the coolant is sucked from the secondcollecting pipe 16 via the connector assembly 25. The coolant is thuspumped/injected into the first collecting pipe 15 with the help of theconveying device 5, and is sucked/discharged from the second collectingpipe 16.

As a result of the heat exchange between the coolant, which flowsthrough the heat exchanger pipes 11 and the collecting pipes 15, 16, andthe air 10, the air 10 is cooled. As a result of the cooling of the air10, condensate accumulates, which can in particular deposit on thebottom 17 of the respective collecting pipe 15, 16. As can in particularbe gathered from FIGS. 3 and 4, wherein FIG. 4 only shows the collectingtank 14 in cross section, the bottoms 17 of the collecting pipes 15, 16run at an incline relative to one another in the manner of a gabled roofor of an upside-down channel, so that they form a predetermined angle26, hereinafter also referred to as angle α, of not equal to 180°, inparticular between 171° and 177°, advantageously of approx. 174°. Therespective bottom 17 is thereby inclined relative to the transversedirection 21, wherein said angle 26 is formed by the outer surface 27 ofthe bottoms 17 facing the heat exchanger pipes 11, which, with theexception of the tank accommodations 24, run in an essentially plane andin a plate-shaped manner, so that the bottoms 17 are each embodied as aplane plate 28. In an installation position 29 or use position 29, whichis illustrated for example in FIGS. 3 and 4, the bottoms 17 are therebyalso inclined relative to the gravitational direction G in such a waythat, in the cross section with the gravitational direction G, they forman angle of smaller than 90°. In other words, the outer surfaces 27 ofboth bottoms 17 are inclined relative to the gravitational direction Gin the installation position 29, so that condensate accumulating on thebottoms 17 can flow along the outer surface 27 in a simplified mannerand can thus be discharged in a simplified manner. In the case of theexample shown in FIGS. 3 and 4, both bottoms 17 are thereby inclined tothe corresponding hollow space 19, so that the bottoms 17 or the outersurfaces 27, respectively, form an angle 26 of smaller than 180°, inparticular of 174°, on the side facing the hollow spaces 19 or facingaway from the heat exchanger pipes 11, respectively. The accumulatingcondensate can thus flow all the way to the central area 22. Thisaccumulating condensate can then flow in the central area 22 or betweenthe heat exchanger pipes 11, which are adjacent in the transversedirection 21, respectively, in the direction of the opposite, lowercollecting tank 14, which is not shown, and can flow there to theoutside from the central area 22 of this collecting tank in thetransverse direction 21, where the condensate can flow away and/or isdischarged.

It can in particular be seen in FIGS. 3 to 5 that the tankaccommodations 24 of the respective bottom 17 or of the collecting pipe14, 15, respectively, are each formed by a passage 30, which can beproduced by means of a tearing of the corresponding bottom 17. It can beseen thereby that the passages 30 are each directed away from thecorresponding hollow space 19 and thus do not penetrate into the hollowspace 19. It is in particular possible hereby to insert the heatexchanger pipes 11 into the collecting pipes 14, 15 with a smallerpenetration depth, so that the volume of the hollow space 19, which canbe flown through or which can be used, respectively, is increased. Itcan furthermore be gathered in particular from FIGS. 3 and 4 that thepassages 30 have front sides 31, which face away from the correspondinghollow space 19, wherein the front sides 31 run in a curved manner inthe transverse direction 21, in particular curved in the shape of acircular segment. As can be gathered from FIG. 3, a reduced contact arearesults between the front side 31 and the adjacent corrugated fin 13 atthe area of the front side 31, which protrudes the most. This volume canthus also be improved and can be used more efficiently for providingwith the corrugated fins 13.

As follows in particular from FIGS. 3 to 5, the collecting tank 14 inthe shown example is produced integrally from one sheet metal part 32 orby forming the sheet metal part 32, respectively. It can further be seenthat the wall 18 of the respective collecting pipe 15, 16 has a circularsection 33 in the shape of a circular segment located opposite thecorresponding bottom 17, as well as transition sections 34, whichconnect to the circular section 33 on both sides and which transitioninto the bottom 17, wherein the circular section 33 and the transitionsections 34 define a flow cross section 35 of the correspondingcollecting pipe 15, 16 or the corresponding hollow space 19,respectively. The flow cross section 35 is thereby preferably Ω-shapedor is close to an Ω-shape, respectively, in the area of the circularsection 33 and in the adjacent area of the corresponding transitionsections 34. In the central area 22, a transition section 34 each ofboth collecting pipes 15, 16 adjoin one another and thus form thecentral seam 23.

On the side facing away from the heat exchanger pipes 11, in particularin the area of the wall 18, the respective collecting pipe 15, 16 has aplurality of beads 36, which will also be identified below asreinforcing beads 36. The reinforcing beads 36 are each embodied asindentations 37, which are directed to the outside. The reinforcingbeads 36 run in the transverse direction 21 and are spaced apart fromone another in the longitudinal direction 20. A reinforcing bead 36 ofthe first collecting pipe 15 and a reinforcing bead 36 of the secondcollecting pipe 16 thereby each meet in the central area 22 of thecollecting tank 14 or in the area of the central seam 23, respectively,in which the transition sections 34 of the collecting pipes 15, 16adjoin one another. An improved mechanical stability of the entirecollecting tank is thus attained, also outside of the beads 36, inparticular also in a height direction 47, which runs transversely to thelongitudinal direction 20 and transversely to the transverse direction21.

According to FIG. 2 as well as FIGS. 6 and 7, the connector assembly 25has a base plate 38 as well as an outer shell 39. The base plate 38 hasa first plate opening 40 and a second plate opening 41. The base plate38 abuts on a front side 46 of a pipe bundle 42, which consists of theheat exchanger pipes 11 and the at least one collecting tank 14. Thefirst plate opening 40 is thereby fluidically connected to a firstcollecting pipe opening 43 on the front side or longitudinal end side,respectively, of the first collecting pipe 15 in a fluidic manner,whereas the second plate opening 41 is fluidically connected to a secondcollecting pipe opening 44 on the front side or longitudinal end side,respectively, of the second collecting pipe 16. The respective plateopening 40, 41 is embodied as an aperture 45 in the base plate 38. Thebase plate 38 extends in the transverse direction 21 as well as in theheight direction 47 and abuts on the front side 46 of the collectingtank 14 as well as on the adjacent, outer corrugated fin 13. On the endof the base plate 38, which is spaced apart from the collecting tank 14,a first plate molding 48 protrudes from the corrugated fin 13 in thetransverse direction 21, and a second plate molding 49 adjacent theretoin the height direction 48 and offset to the collecting tank 14. Theouter shell 39 follows the course of the base plate 38 and has a firstshell molding 50 located opposite the first plate molding 48, and asecond shell molding 51 located opposite the second plate molding 49.The first plate molding 48, together with the first shell molding 50,forms a first pipe accommodation 42 for a first supply pipe body 53,whereas the second plate molding 49 forms, with the second shell molding51, a second pipe accommodation 54, which is separate from the firstpipe accommodation 52 and is spaced apart in the height direction 47,for a second supply pipe body 55 of the assembly 25. The respectivesupply pipe body 53, 55 has a pipe-shaped adapter element 56, which isaccommodated in the corresponding pipe accommodation 52, 54 and isenclosed in a positive manner in such a way that the supply pipe body53, 55 is fastened in the corresponding pipe accommodation 52, 54 in amechanically stable manner. Even through the respective supply pipe body53, 55 is illustrated so as to be spaced apart from the correspondingadapter element 56 in FIG. 6, the respective supply pipe body 53, 55 andthe corresponding adapter element 56 can be made integrally, inparticular monolithically, so that no separate connection between theadapter element 56 and the corresponding supply body 53, 55 isnecessary.

The first supply pipe body 53 is fluidically connected to the firstplate opening 40 and thus to the first collecting pipe 15 via a firstsupply duct 57 connected to the first accommodation 52. In contrast, thesecond supply pipe body 55 is fluidically connected to the second plateopening 41 and thus to the second collecting pipe 16 via the second pipeaccommodation 54 and a second supply duct 58, which is separated fromthe first supply duct 57. Coolant is thus introduced into the firstaccumulating pipe 15 via the first supply pipe body 53, whereas coolantis sucked from the second collecting pipe 16 via the second supply pipebody 55. The respective supply duct 57, 58 thereby connects to thecorresponding pipe accommodation 52, 54, and is formed by the base plate38 as well as a duct section 59 of the outer shell 39, which is embodiedby a molding.

As can in particular be gathered from FIG. 6, the first plate opening 40is smaller, has in particular a smaller cross section than the secondplate opening 41. It can further be seen that the second plate opening41 has a shape, which is adapted to the circular section 33 of thesecond collecting pipe 16 in the area of the second collecting pipeopening 44, or an adapted cross section, respectively. This means inparticular that the cross section of the second plate opening 41 isembodied complementary to the cross section of the second collectingpipe opening 44. The coolant can thereby be sucked from the secondcollecting pipe 16 particularly effectively and with little loss ofpressure.

FIG. 8 shows a further exemplary embodiment of the base plate 38, in thecase of which the second plate opening 41 has a cross section, whichcorresponds to the flow cross section 35 of the second collecting pipe16 in FIGS. 3 and 4, which, in the case of the shown example, preferablyalso corresponds to the flow cross section 35 of the second collectingpipe opening 44. It can further be seen in FIG. 8 that the plateopenings 40, 41 are each arranged in a depression 60, which is directedtowards the collecting tank 14, wherein the depressions 60 each slightlypenetrate into the corresponding collecting pipe opening 43, 44 and havea form filling one of the corresponding collecting opening 43, 44. Thesecond plate opening 41 is thereby embodied in the entire correspondingdepression 60, whereas the first plate opening 40 has a round form andis arranged approximately in the center in the corresponding depression60. It can also be seen that the depressions 60 follow the inclinedcourse of the bottoms 17.

In the case of the exemplary embodiment shown in FIG. 8, the first platemolding 48 differs from the second plate molding 49, so that the firstpipe accommodation 52 also differs from the second pipe accommodation54. The adapter element 56 of the first supply pipe body 53 and theadapter element 56 of the second supply pipe body 55 are thus embodieddifferently in this exemplary embodiment. In contrast, the respectivepipe accommodation 52, 54 is embodied identically in FIGS. 2, 6 and 7,so that the adapter elements 56 of both supply pipe bodies 53, 55 areembodied identically as well. It can further be seen in FIG. 6 that thefirst supply pipe body 53 outside of the corresponding adapter element56 is smaller than the second supply pipe body 55 and has acorrespondingly smaller flow cross section.

The base plate 38, the outer shell 39 as well as the supply pipe bodies53, 55, in particular the adapter elements 56, are preferably joinedintegrally to one another by means of a joint process, whereby it ispreferred when they are soldered to one another. For this purpose, theouter shell 39 and the base plate 38 can be solder-plated at least onone side. The respective adapter element 56 can thereby be placed in thecorresponding plate molding 48, 49, and the outer shell 39 cansubsequently be brought into contact with the base plate 38, and can befixed thereto so as to attain the form of the connector assembly 25shown in FIGS. 2 and 7, wherein the assembly 25 is joined integrallysubsequently, in particular soldered. It is also conceivable to join theassembly 25 integrally, in particular to weld it, together with furtherparts of the heat exchanger 9. In addition to the production of theconnector assembly 25, a connection of the connector assembly 25 to theremaining heat exchanger 9 is simultaneously attained as well thereby.In this case, as little solder as possible is attached to the side ofthe base plate 38 facing away from the outer shell 39, in particular asolder-plating comprising a solder portion of less than 5%, so as toprevent or so as to at least reduce a combustion or damages,respectively, to the adjacent corrugated fin 13.

As can in particular be gathered from FIGS. 2, 6 and 7, the outer shell39 has, in the area of the plate openings 40, 41, a handle section 61,which protrudes on the edge side, follows the form of the collectingtank 41 and of the base plate 38, and which protrudes beyond the baseplate 38 on the edge side. The handle section 61 encompasses the frontside 46 of the collecting tank 14 on the edge side and is mechanicallyconnected to the collecting tank 14 via a plurality of connectingelements 62, which are arranged so as to be distributed and whichinteract in a positive manner with mating connecting elements 63provided on the walls 18 of the collecting pipes 15, 16. The collectingpipe openings 43, 44 and the base plate 38 are thereby encompassed bythe handle section 61 on the edge side, because the handle section 61abuts on the outer side of the wall 18 of the respective collecting pipe15, 16. This stabilizes the connection between the collecting tank 14and the connector assembly 25 and leads to smaller pressure losses inthe coolant or to an improved sealing, respectively, of the flow path ofthe coolant. The connecting elements 62 and mating connecting elements63 can further be used to fix the assembly 25 in a relative manner tothe remaining heat exchanger 9 prior to an integral joining.

In the case of the shown examples, both pipe accommodations 52, 54extend along the base plate 38, so that they are orientedperpendicularly to the corresponding plate opening 40, 41 or so that thepipe accommodations 52, 54 can each be flown through in a plane, whichruns perpendicular to the corresponding plate opening 40, 41,respectively. The respective supply duct 57, 58 thereby runs in a curvedmanner, in particular by 90°.

As shown in FIG. 3, the collecting tank 14 has a tank height 65, whichruns in the height direction 47, which can be less than 48 mm, inparticular less than 46 mm, for example between 40 mm and 43 mm, inparticular 42 mm. A corresponding height 66 of the passages 30,hereinafter referred to as passage height 66, can be less than 3 mm,preferably less than 2.5 mm and 2.2 mm, particularly preferably 2 mm.

A height 76, which runs in the height direction 47, of a net 75, whichconsists of the heat exchanger pipes 11 and corrugated fins 13, of theheat exchanger 9, also referred to as net height 76 (see also FIG. 7) ispreferably less than 45 mm, in particular less than 42 mm.Advantageously, the net height 76 is between 39 mm and 40 mm, inparticular between 39.4 mm and 40 mm.

1. A collecting tank of a heat exchanger, comprising: a first collectingpipe and a second collecting pipe arranged adjacent to the firstcollecting pipe structured to accommodate a plurality of heat exchangerpipes, the first collecting pipe and the second collecting pipe eachhaving a hollow space which is flowable through; the first collectingpipe and the second collecting pipe having a respective flattenedbottom; and a plurality of tank accommodations configured to accommodatethe plurality of heat exchanger pipes disposed spaced apart from oneanother in the respective bottom of the first collecting pipe and thesecond collecting pipe; wherein the respective bottom of the firstcollecting pipe and the second collecting pipe extend at a predeterminedangle α not equal to 180° relative to one another.
 2. The collectingtank according to claim 1, wherein the predetermined angle α is from177° to 171°.
 3. The collecting tank according to claim 1, wherein therespective bottoms of the first collecting pipe and the secondcollecting pipe is structured as a plane plate.
 4. The collecting tankaccording to claim 1, wherein the respective bottoms of the firstcollecting pipe and the second collecting pipe is inclined towards acorresponding hollow space.
 5. The collecting tank according to claim 1,wherein the predetermined angle α is greater than 180°, and wherein therespective bottom of the first collecting pipe and the second collectingpipe is inclined away from a corresponding hollow space.
 6. Thecollecting tank according to claim 1, wherein at least one of the firstcollecting pipe and the second collecting pipe includes a wall coupledto the respective bottom and defining a flow cross section with therespective bottom.
 7. The collecting tank according to claim 6, whereinthe wall has a circular section in the shape of a circular segmentdisposed opposite the respective bottom and a plurality of transitionsections connected thereto on both sides, which transition into therespective bottom.
 8. The collecting tank according to claim 1, whereinthe plurality of tank accommodations of the respective bottom of atleast one of the first collecting pipe and the second collecting pipeare defined by a plurality of passages directed away from acorresponding hollow space.
 9. The collecting tank according to claim 8,wherein at least one of the plurality of passages protrudes from therespective bottom by less than 3 mm.
 10. The collecting tank accordingto claim 8, wherein at least one of the plurality of passages has apassage front side extending in a curved manner.
 11. The collecting tankaccording to claim 1, wherein: the first collecting pipe and the secondcollecting pipes each have a plurality of beads disposed on a respectiveside arranged opposite the respective bottom; and a bead of the firstcollecting pipe and a bead of the second collecting pipe are inmechanical contact in an area between the first collecting pipe and thesecond collecting pipes.
 12. The collecting tank according to claim 1,wherein the first collecting pipe and the second collecting pipe areintegrally provided as a single sheet metal part.
 13. A heat exchangercomprising: at least one collecting tank including: a first collectingpipe and a second collecting pipe arranged adjacent to the firstcollecting pipe each having a hollow space which is flowable through;the first collecting pipe and the second collecting pipe having arespective flattened bottom; and a plurality of tank accommodationsdisposed spaced apart from one another in the respective bottom of thefirst collecting pipe and the second collecting pipe; a plurality ofheat exchanger pipes accommodated in the plurality of tankaccommodations of the respective bottoms of the first collecting pipeand the second collecting pipe; wherein the respective bottom of thefirst collecting pipe and the second collecting pipe extend relative toone another at a predetermined angle α not equal to 180°.
 14. The heatexchanger according to claim 13, wherein at least one of the firstcollecting pipe and the second collecting pipe includes a wall coupledto the respective bottom and defining a flow cross section with therespective bottom.
 15. The heat exchanger according to claim 13, whereinthe plurality of tank accommodations of the respective bottom of atleast one of the first collecting pipe and the second collecting pipeare defined by a plurality of passages directed away from acorresponding hollow space.
 16. The heat exchanger according to claim15, wherein at least one of the plurality of passages protrudes from therespective bottom by less than 3 mm.
 17. The collecting tank accordingto claim 2, wherein the predetermined angle α is 174°.
 18. A collectingtank of a heat exchanger comprising: a first collecting pipe and asecond collecting pipe arranged adjacent thereto each defining arespective hollow space through which a flow is flowable, the firstcollecting pipe and the second collecting pipe including a respectiveflattened bottom, a respective wall coupled to the respective bottom,and a flow cross section defined between the respective wall and therespective bottom; and a plurality of tank accommodations disposedspaced apart in the respective bottom configured to accommodate aplurality of heat exchanger pipes; wherein the respective bottom of thefirst collecting pipe and the second collecting pipe extend transverselyto one another at a predetermined angle α.
 19. The collecting tankaccording to claim 18, wherein the predetermined angle α is greater than180°, and wherein the respective bottom of the first collecting pipe andthe second collecting pipe is inclined away from a corresponding hollowspace.
 20. The collecting tank according to claim 18, wherein thepredetermined angle α is 171° to 177°, and wherein the respective bottomof the first collecting pipe and the second collecting pipe is inclinedtowards a corresponding hollow space.